JP6570965B2 - Absorption heat pump - Google Patents

Description

  The present invention relates to an absorption heat pump, and more particularly to an absorption heat pump that suppresses an increase in pressure inside an absorber can body without providing a safety valve.

  As a heat source machine for taking out a heated medium having a temperature higher than the driving heat source temperature, there is a second type absorption heat pump. The second type absorption heat pump mainly includes an evaporator for evaporating the refrigerant liquid, an absorber for absorbing the refrigerant vapor with the absorbing liquid, a regenerator for removing the refrigerant from the absorbing liquid, and a condenser for condensing the refrigerant vapor. The internal pressure of the regenerator and the absorber is operated in a state higher than the internal pressure of the regenerator and the condenser. In the absorption heat pump machine, measures to avoid an excessive pressure rise are applied to a portion that can be higher than the atmospheric pressure. As an example, in the second type absorption heat pump, there is one in which a safety valve is provided in a heated medium vapor pipe to which a heated medium generated by pumping and heating heat is supplied to the outside (for example, Patent Document 1). reference.).

JP2013-253748A (FIG. 1 etc.)

  The heat pump described in Patent Document 1 is provided with a safety valve in a heated medium vapor pipe to which a heated medium is supplied to the outside. However, depending on operating conditions such as the temperature of a heat source to be introduced, an evaporator and an absorption The internal pressure of the vessel may exceed atmospheric pressure. In the case of a configuration in which a plurality of evaporators and absorbers are provided to raise the temperature in multiple stages, the internal pressure of the evaporator and absorber on the high pressure side may exceed the atmospheric pressure. In such cases, measures are taken to avoid excessive pressure rises in the evaporator and absorber systems that may exceed atmospheric pressure. However, if a safety valve is provided in the evaporator / absorber system, air may enter the interior when the operation of the heat pump is stopped and a negative pressure is reached. If air enters the evaporator or the absorber, corrosion may occur inside.

  In view of the above-described problems, an object of the present invention is to provide an absorption heat pump that suppresses an increase in pressure inside an absorber can body without providing a safety valve.

  In order to achieve the above object, the absorption heat pump according to the first aspect of the present invention includes a heated fluid channel 11 (31, 51) and a heated fluid channel 11 (31, as shown in FIG. 1, for example. , 51), the absorbent supply unit 12 (32, 52) for supplying the absorbent Sa (Sb, Sc), the heated fluid channel 11 (31, 51), and the absorbent supply unit 12 (32, 52). ) And the absorption liquid Sa (Sb, Sc) supplied from the absorption liquid supply unit 12 (32, 52) is the refrigerant vapor Va (Vb, Vc). Absorber 10 (30, 50) that heats the fluid Wq (Vf, Vf) that flows through the heated fluid flow path 11 (31, 51) with the absorption heat generated when absorbing the refrigerant); The dilute solution Sw, which is an absorbing solution whose concentration has been reduced by absorbing the vapor Vc, is introduced. A regenerator 70 for heating and releasing the refrigerant from the dilute solution Sw to increase the concentration of the absorbing solution Sw; and the absorbing solution Sa having a concentration higher than that of the dilute solution Sw in the regenerator 70 is guided to the absorbing solution supply unit 12. Concentrated solution transport parts 75 and 76; a condenser 80 that introduces the refrigerant vapor Vg separated from the dilute solution Sw in the regenerator 70, cools and condenses it, and generates a refrigerant liquid Vf; An evaporator 20 (40, 60) that introduces the refrigerant liquid Vf, which is heated and evaporated to generate refrigerant vapor Va (Vb, Vc) to be supplied to the absorber 10 (30, 50); The refrigerant liquid conveying parts 82, 84, 86, 88, 89 for guiding the refrigerant liquid Vf of the condenser 80 to the evaporator 20 (40, 60); or the internal pressure of the absorber can body 14 (34, 54) directly or Indirectly detecting pressure detector 14P (34 , 54P); When the pressure detected by the pressure detector 14P (34P, 54P) is equal to or higher than a predetermined pressure, the absorption liquid Sa (Sb, Sc) is introduced into the absorption liquid supply unit 12 (32, 52). And a control device 100 that stops at least one of introduction of the refrigerant liquid Vf to the evaporator 20 (40, 60).

  With this configuration, when the pressure detected by the pressure detector is equal to or higher than a predetermined pressure, the generation of absorption heat that can increase the internal pressure of the absorber can body and the refrigerant vapor supplied to the absorber At least one of the occurrences can be stopped, and an increase in pressure inside the absorber can body can be suppressed without providing a safety valve.

  In addition, the absorption heat pump according to the second aspect of the present invention is, for example, as shown in FIG. 1, in the absorption heat pump 1 according to the first aspect of the present invention, the control device 100 includes a pressure detector 14P (34P, When the pressure detected at 54P) is equal to or higher than a predetermined pressure, the absorption of the refrigerant liquid Vf into the evaporator 20 (40, 60) is stopped and the absorption into the absorption liquid supply unit 12 (32, 52) is stopped. The introduction of the liquid Sa (Sb, Sc) is continued.

  With this configuration, the refrigerant vapor generated in the evaporator quickly decreases, while the absorber absorbs the refrigerant vapor, so the amount of refrigerant vapor in the absorber can body decreases rapidly and is absorbed. The pressure in the can body can be quickly reduced.

  Moreover, the absorption heat pump according to the third aspect of the present invention is, for example, as shown in FIG. 1, in the absorption heat pump 1 according to the first aspect or the second aspect of the present invention, the absorber is a high-temperature absorber. 10 and a low-temperature absorber 50 having an operating pressure lower than that of the high-temperature absorber 10; the evaporator includes a high-temperature evaporator 20 and a low-temperature evaporator 60 having an operating pressure lower than that of the high-temperature evaporator 20. The refrigerant vapor Vc generated in the low-temperature evaporator 60 is introduced into the low-temperature absorber 50 and the refrigerant vapor Va generated in the high-temperature evaporator 20 is introduced into the high-temperature absorber 10. The pressure detectors 14P and 54P are configured to directly or indirectly detect the internal pressures of the absorber can bodies 14 and 54 of the high-temperature absorber 10 and the low-temperature absorber 50, respectively. , High temperature absorber 10 It is set separately for the low temperature absorber 50.

  If comprised in this way, each absorber can body of a high-temperature absorber and a low-temperature absorber is comprised individually so that it may be suitable for an operating pressure, and the internal pressure of each absorber can body is permitted, reducing the weight of an absorption heat pump. When the pressure rises close to the pressure, the pressure rise can be suppressed.

  Moreover, the absorption heat pump according to the fourth aspect of the present invention is controlled in the absorption heat pump 1 according to any one of the first to third aspects of the present invention as shown in FIG. When the pressure detected by the pressure detector 14P (34P, 54P) is equal to or higher than a predetermined pressure, the apparatus 100 introduces a part or all of the heating source hg to the regenerator 70, and the heating source to the evaporator 60. At least one of the introduction of part or all of he and the introduction of part or all of the cooling source to the condenser 80 is stopped.

  If comprised in this way, generation | occurrence | production of absorption heat and generation | occurrence | production of the vapor | steam of the refrigerant | coolant supplied to an absorber can be suppressed, and it will contribute to suppression of the pressure rise inside an absorber can body.

  In addition, the absorption heat pump according to the fifth aspect of the present invention is the same as the absorption heat pump 1 according to any one of the first to fourth aspects of the present invention, as shown in FIG. The refrigerant liquid introduction portions 78 and 78v that allow the refrigerant liquid Vf of the regenerator 80 to be introduced into the regenerator 70 are provided; the control device 100 has a predetermined pressure detected by the pressure detector 14P (34P and 54P). When the pressure is equal to or higher than the pressure, introduction of the refrigerant liquid Vf of the condenser 80 into the regenerator 70 is started.

  With this configuration, by stopping the introduction of the refrigerant liquid into the evaporator and introducing into the regenerator an absorption liquid that does not reduce the concentration without the refrigerant vapor being introduced into the absorber, and / or When the concentration of the absorbing liquid introduced into the regenerator becomes high by stopping the introduction of the absorbing liquid into the absorber and stopping the flow of the absorbing liquid in the regenerator, the concentration of the absorbing liquid in the regenerator Can be reduced.

  According to the present invention, when the pressure detected by the pressure detector is equal to or higher than a predetermined pressure, the generation of absorption heat that can increase the internal pressure of the absorber can body and the vapor of the refrigerant supplied to the absorber. At least one of the occurrences can be stopped, and an increase in pressure inside the absorber can body can be suppressed without providing a safety valve.

1 is a schematic system diagram of an absorption heat pump according to an embodiment of the present invention. (A) is a graph showing an example of changes in the internal pressure of the gas-liquid separator and the absorber can body when the introduction of the absorbing liquid into the absorber is continued while stopping the introduction of the refrigerant liquid into the evaporator; ) Is a graph showing an example of changes in internal pressure of the gas-liquid separator and the absorber can body when the introduction of the refrigerant liquid into the evaporator is continued while the introduction of the absorbent into the absorber is stopped.

  Embodiments of the present invention will be described below with reference to the drawings. In the drawings, the same or similar members are denoted by the same or similar reference numerals, and redundant description is omitted.

  First, an absorption heat pump 1 according to an embodiment of the present invention will be described with reference to FIG. FIG. 1 is a schematic system diagram of the absorption heat pump 1. The absorption heat pump 1 is a three-stage temperature rising type absorption heat pump. In the present embodiment, the absorption heat pump 1 introduces, as a heat source medium, low-temperature (for example, about 80 ° C. to 90 ° C.) low-temperature (for example, about 80 ° C. to 90 ° C.) waste heat water hev, which has a relatively low utility value. , A second type absorption heat pump that can take out a pressure exceeding about 0.2 MPa (gauge pressure), desirably about 0.8 MPa (gauge pressure). The absorption heat pump 1 includes a high temperature absorber 10, a high temperature evaporator 20, an intermediate temperature absorber 30, an intermediate temperature evaporator 40, a low temperature absorber 50, a low temperature evaporator 60, and a regenerator 70 as main components. The condenser 80 is provided. In addition, the absorption heat pump 1 includes a control device 100.

In the following description, regarding the absorbing liquid (sometimes referred to as “solution”), in order to facilitate the distinction on the heat pump cycle, the “high concentration solution Sa”, depending on the properties and the position on the heat pump cycle, Although referred to as “medium concentration solution Sb”, “low concentration solution Sc”, “dilute solution Sw”, etc., when the properties are not questioned, they are collectively referred to as “absorbing solution S”. Similarly, in order to easily distinguish the refrigerant on the heat pump cycle, “high temperature refrigerant vapor Va”, “medium temperature refrigerant vapor Vb”, “low temperature refrigerant vapor Vc”, “ Although referred to as “regenerator refrigerant vapor Vg”, “refrigerant liquid Vf”, etc., when the properties are not questioned, they are collectively referred to as “refrigerant V”. In the present embodiment, an LiBr aqueous solution is used as the absorbing liquid S (a mixture of the absorbent and the refrigerant V), and water (H ₂ O) is used as the refrigerant V. Moreover, it is comprised so that the to-be-heated water vapor | steam Wv may be supplied from the absorption heat pump 1 to the exterior as a product (target object). The heated water vapor Wv is obtained by evaporating the heated water liquid Wq, and is referred to as heated water W when these properties are not questioned. In the present embodiment, water (H ₂ O) is used as the heated water W.

  The high-temperature absorber 10 has a heat transfer tube 11 constituting a flow path of the water to be heated W and a high-concentration solution spray nozzle 12 for spraying the high-concentration solution Sa inside the high-temperature absorber can body 14. . The heat transfer tube 11 corresponds to a heated fluid channel, the high-concentration solution spray nozzle 12 corresponds to an absorbent supply unit, and the high-temperature absorber can body 14 corresponds to an absorber can body. The high-concentration solution spray nozzle 12 is disposed above the heat transfer tube 11 so that the sprayed high-concentration solution Sa falls on the heat transfer tube 11. The high temperature absorber 10 generates heat of absorption when the high concentration solution Sa is sprayed from the high concentration solution spray nozzle 12 and the high concentration solution Sa absorbs the high temperature refrigerant vapor Va. The heated water W flowing through the heat transfer tube 11 receives this absorbed heat, and the heated water W is heated. In the high-temperature absorber 10, the heated water W flowing inside the heat transfer tube 11 corresponds to the heated fluid. In the lower part of the high-temperature absorber 10, a storage part 13 in which the medium concentration solution Sb is stored is formed. The medium concentration solution Sb is an absorbing solution S whose concentration is lowered from the high concentration solution Sa because the high concentration solution Sa sprayed from the high concentration solution spray nozzle 12 absorbs the high-temperature refrigerant vapor Va. The heat transfer tube 11 is disposed above the storage portion 13 so as not to be immersed in the medium concentration solution Sb. If it does in this way, the absorbed heat which generate | occur | produced will be rapidly transmitted to the to-be-heated water W which flows through the inside of the heat exchanger tube 11, and recovery | restoration of absorption capability can be accelerated. The high-temperature absorber can body 14 has a thickness that can withstand a pressure obtained by adding a margin to the design operating pressure. The high temperature absorber can body 14 is provided with a high temperature absorber pressure gauge 14P as a pressure detector for detecting the internal pressure.

  The high-temperature evaporator 20 is a component that supplies the high-temperature refrigerant vapor Va to the high-temperature absorber 10. The high-temperature evaporator 20 includes a refrigerant gas-liquid separation cylinder 21 that stores the refrigerant liquid Vf and the high-temperature refrigerant vapor Va, a high-temperature refrigerant liquid supply pipe 22, and a high-temperature refrigerant vapor receiving pipe 24. The high-temperature refrigerant liquid supply pipe 22 is a pipe constituting a flow path that guides the refrigerant liquid Vf to the heating pipe 31 of the intermediate temperature absorber 30. The high-temperature refrigerant vapor receiving pipe 24 represents the refrigerant gas-liquid mixed phase of the high-temperature refrigerant vapor Va generated by the refrigerant liquid Vf being heated by the heating pipe 31 of the intermediate temperature absorber 30 or the high-temperature refrigerant vapor Va and the refrigerant liquid Vf. It is a tube constituting a flow path for guiding to the separation cylinder 21. A baffle plate (not shown) that collides and separates the droplets of the refrigerant V contained in the high-temperature refrigerant vapor Va is provided in the refrigerant gas-liquid separation cylinder 21. In the present embodiment, the inner surface of the heating tube 31 of the intermediate temperature absorber 30 is used as the heat transfer surface of the high temperature evaporator 20. The high temperature evaporator 20 is connected to a refrigerant liquid pipe 82 for introducing the refrigerant liquid Vf. A flow rate adjustment valve 83 is disposed in the refrigerant liquid pipe 82 connected to the high temperature evaporator 20. One end of the high-temperature refrigerant liquid supply pipe 22 is connected to the portion of the refrigerant gas-liquid separation cylinder 21 where the refrigerant liquid Vf is stored, and the other end is connected to one end of the heating pipe 31. The high temperature refrigerant vapor receiving pipe 24 has one end connected to the refrigerant gas-liquid separation cylinder 21 and the other end connected to the other end of the heating pipe 31. In the high-temperature evaporator 20, the refrigerant liquid Vf changes to steam inside the heating pipe 31 and the density is greatly reduced. Therefore, the refrigerant in the refrigerant gas-liquid separation cylinder 21 is assumed to function as the bubble pump. A pump for sending the liquid Vf to the heating pipe 31 is omitted. A pump (not shown) that sends the refrigerant liquid Vf in the refrigerant gas-liquid separation cylinder 21 to the heating pipe 31 may be disposed in the high-temperature refrigerant liquid supply pipe 22.

  The high temperature evaporator 20 and the high temperature absorber 10 are connected by a high temperature refrigerant vapor pipe 29 as a high temperature refrigerant vapor flow path. One end of the high-temperature refrigerant vapor pipe 29 is connected to the upper part (typically the top) of the refrigerant gas-liquid separation cylinder 21, and the other end is absorbed at a high temperature above the high-concentration solution spray nozzle 12. The container body 14 is connected. With such a configuration, the high-temperature refrigerant vapor Va generated by the high-temperature evaporator 20 can be supplied to the high-temperature absorber 10 through the high-temperature refrigerant vapor pipe 29. Further, the high-temperature absorber 10 and the high-temperature evaporator 20 communicate with each other via the high-temperature refrigerant vapor pipe 29, so that the internal pressure becomes substantially the same.

  The intermediate temperature absorber 30 includes a heating pipe 31 constituting a flow path for the refrigerant liquid Vf and the high temperature refrigerant vapor Va and an intermediate concentration solution spray nozzle 32 inside the intermediate temperature absorber can body 34. The heating tube 31 corresponds to a heated fluid flow path, the medium concentration solution spray nozzle 32 corresponds to an absorbent supply unit, and the intermediate temperature absorber can body 34 corresponds to an absorber can body. As described above, the heating pipe 31 has one end connected to the high-temperature refrigerant liquid supply pipe 22 and the other end connected to the high-temperature refrigerant vapor receiving pipe 24. The medium concentration solution spray nozzle 32 sprays the medium concentration solution Sb in the present embodiment. The medium concentration solution spray nozzle 32 is disposed above the heating tube 31 so that the sprayed medium concentration solution Sb falls on the heating tube 31. One end of a medium concentration solution tube 15 for flowing the medium concentration solution Sb is connected to the medium concentration solution spray nozzle 32. The intermediate temperature absorber 30 heats the refrigerant liquid Vf flowing through the heating pipe 31 by absorption heat generated when the intermediate concentration solution Sb is applied from the intermediate concentration solution spray nozzle 32 and the intermediate concentration solution Sb absorbs the intermediate temperature refrigerant vapor Vb. Thus, the high-temperature refrigerant vapor Va can be generated. In the intermediate temperature absorber 30, the refrigerant liquid Vf and the high-temperature refrigerant vapor Va flowing inside the heating pipe 31 correspond to the fluid to be heated. The intermediate temperature absorber 30 is configured to operate at a pressure (dew point temperature) lower than that of the high temperature absorber 10, and the operating temperature is lower than that of the high temperature absorber 10. A storage part 33 for storing the low-concentration solution Sc is formed in the lower part of the intermediate temperature absorber 30. The low-concentration solution Sc is an absorbing solution S whose concentration is lowered by the medium-concentration solution Sb sprayed from the medium-concentration solution spray nozzle 32 absorbing the intermediate temperature refrigerant vapor Vb. The heating tube 31 is disposed above the storage unit 33. In addition, the intermediate temperature absorber can body 34 has a thickness that can withstand a pressure obtained by adding a margin to the design operating pressure. Since the operating pressure of the intermediate temperature absorber 30 is lower than the operating pressure of the high temperature absorber 10, the intermediate temperature absorber can body 34 can be made thinner than the high temperature absorber can body 14. The intermediate temperature absorber can body 34 is provided with an intermediate temperature absorber pressure gauge 34P as a pressure detector for detecting the internal pressure.

  The intermediate temperature evaporator 40 is a component that supplies the intermediate temperature refrigerant vapor Vb to the intermediate temperature absorber 30. The intermediate temperature evaporator 40 includes a refrigerant gas-liquid separation cylinder 41 that stores the refrigerant liquid Vf and the intermediate temperature refrigerant vapor Vb, an intermediate temperature refrigerant liquid supply pipe 42, and an intermediate temperature refrigerant vapor receiving pipe 44. The intermediate temperature refrigerant liquid supply pipe 42 is a pipe that constitutes a flow path that guides the refrigerant liquid Vf to the heating pipe 51 of the low temperature absorber 50. The intermediate-temperature refrigerant vapor receiving pipe 44 is a refrigerant gas-liquid that represents an intermediate-temperature refrigerant vapor Vb generated by heating the refrigerant liquid Vf in the heating pipe 51 of the low-temperature absorber 50 or a refrigerant gas-liquid mixed phase of the intermediate-temperature refrigerant vapor Vb and the refrigerant liquid Vf. It is a tube constituting a flow path for guiding to the separation cylinder 41. The refrigerant gas-liquid separation cylinder 41 is configured in the same manner as the refrigerant gas-liquid separation cylinder 21 of the high-temperature evaporator 20. In the present embodiment, the inner surface of the heating tube 51 of the low temperature absorber 50 is used as the heat transfer surface of the intermediate temperature evaporator 40. In addition, a refrigerant liquid pipe 84 for introducing the refrigerant liquid Vf is connected to the intermediate temperature evaporator 40. The refrigerant liquid pipe 84 branches from the refrigerant liquid pipe 82. A flow rate adjustment valve 85 is disposed in the refrigerant liquid pipe 84 connected to the intermediate temperature evaporator 40. The intermediate temperature refrigerant liquid supply pipe 42 has one end connected to the portion of the refrigerant gas-liquid separation cylinder 41 where the refrigerant liquid Vf is stored, and the other end connected to one end of the heating pipe 51. The intermediate temperature refrigerant vapor receiving pipe 44 has one end connected to the refrigerant gas-liquid separation cylinder 41 and the other end connected to the other end of the heating pipe 51. In the intermediate temperature evaporator 40, since the refrigerant liquid Vf changes to steam inside the heating pipe 51 and the density is greatly reduced, the refrigerant in the refrigerant gas-liquid separation cylinder 41 is assumed to function as the bubble pump. A pump for sending the liquid Vf to the heating pipe 51 is omitted. A pump (not shown) that sends the refrigerant liquid Vf in the refrigerant gas-liquid separation cylinder 41 to the heating pipe 51 may be disposed in the intermediate temperature refrigerant liquid supply pipe 42.

  The intermediate temperature evaporator 40 and the intermediate temperature absorber 30 are connected by an intermediate temperature refrigerant vapor pipe 49 as an intermediate temperature refrigerant vapor channel. One end of the intermediate temperature refrigerant vapor pipe 49 is connected to the upper part (typically the top) of the refrigerant gas-liquid separation cylinder 41, and the other end is above the intermediate concentration solution spray nozzle 32 and absorbs the intermediate temperature. The container body 34 is connected. With such a configuration, the intermediate temperature refrigerant vapor Vb generated by the intermediate temperature evaporator 40 can be supplied to the intermediate temperature absorber 30 via the intermediate temperature refrigerant vapor pipe 49. Further, the intermediate temperature absorber 30 and the intermediate temperature evaporator 40 communicate with each other via the intermediate temperature refrigerant vapor pipe 49, and therefore have substantially the same internal pressure.

  The low-temperature absorber 50 has a heating pipe 51 that constitutes a flow path for the refrigerant liquid Vf and the medium-temperature refrigerant vapor Vb, and a low-concentration solution spray nozzle 52 inside the low-temperature absorber can body 54. The heating pipe 51 corresponds to a fluid flow path to be heated, the low-concentration solution spray nozzle 52 corresponds to an absorbent supply unit, and the low-temperature absorber can body 54 corresponds to an absorber can body. As described above, the heating pipe 51 is connected to the intermediate temperature refrigerant liquid supply pipe 42 at one end and the intermediate temperature refrigerant vapor receiving pipe 44 at the other end. The low concentration solution spray nozzle 52 sprays the low concentration solution Sc in the present embodiment. The low concentration solution spray nozzle 52 is disposed above the heating tube 51 so that the sprayed low concentration solution Sc falls on the heating tube 51. The low concentration solution spray nozzle 52 is connected to one end of a low concentration solution pipe 35 that allows the low concentration solution Sc to flow inside. The low-temperature absorber 50 sprays the low-concentration solution Sc from the low-concentration solution spray nozzle 52, and heats the refrigerant liquid Vf flowing through the heating pipe 51 by heat absorbed when the low-concentration solution Sc absorbs the low-temperature refrigerant vapor Vc. Thus, the intermediate temperature refrigerant vapor Vb can be generated. In the low temperature absorber 50, the refrigerant liquid Vf and the intermediate temperature refrigerant vapor Vb flowing inside the heating pipe 51 correspond to the fluid to be heated. The low temperature absorber 50 is configured to operate at a pressure (dew point temperature) lower than that of the intermediate temperature absorber 30, and the operating temperature is lower than that of the intermediate temperature absorber 30. A storage part 53 for storing the dilute solution Sw is formed below the low-temperature absorber 50. The dilute solution Sw is an absorbing solution S whose concentration is lowered by absorbing the low-temperature refrigerant vapor Vc by the absorbing solution S (low concentration solution Sc in the present embodiment) sprayed from the low concentration solution spray nozzle 52. The dilute solution Sw contains more refrigerant V than the high concentration solution Sa and the medium concentration solution Sb. The heating tube 51 is disposed above the storage unit 53. The low temperature absorber can body 54 has a thickness that can withstand a pressure obtained by adding a margin to the design operating pressure. Since the operating pressure of the low temperature absorber 50 is lower than the operating pressure of the intermediate temperature absorber 30, the low temperature absorber can body 54 can be made thinner than the intermediate temperature absorber can body 34. The low-temperature absorber can body 54 is provided with a low-temperature absorber pressure gauge 54P as a pressure detector for detecting the internal pressure.

  The low-temperature evaporator 60 includes therein a heat source pipe 61 that forms a flow path of the evaporator heat source hot water he as an evaporator heat source fluid, and a refrigerant liquid spray nozzle 62 that sprays the refrigerant liquid Vf. The refrigerant liquid spray nozzle 62 is disposed above the heat source pipe 61 so that the sprayed refrigerant liquid Vf falls on the heat source pipe 61. One end of a refrigerant liquid pipe 86 for flowing the refrigerant liquid Vf to the inside is connected to the low temperature evaporator 60. The refrigerant liquid pipe 86 is provided with a flow rate adjusting valve 87 for adjusting the flow rate of the refrigerant liquid Vf introduced into the low temperature evaporator 60. One end of a low-temperature refrigerant liquid pipe 65 that guides the refrigerant liquid Vf stored in the lower part of the low-temperature evaporator 60 to the refrigerant liquid spray nozzle 62 is connected to the lower part (typically the bottom part) of the low-temperature evaporator 60. The other end of the low-temperature refrigerant liquid pipe 65 is connected to the refrigerant liquid spray nozzle 62. The low-temperature refrigerant liquid pipe 65 is provided with a low-temperature refrigerant liquid pump 66 that pumps the refrigerant liquid Vf flowing inside. In the low-temperature evaporator 60, the refrigerant liquid Vf is sprayed from the refrigerant liquid spray nozzle 62, and the sprayed refrigerant liquid Vf is evaporated by the heat of the evaporator heat source hot water he flowing in the heat source pipe 61 to generate the low-temperature refrigerant vapor Vc. It is configured as follows. The evaporator heat source hot water he serves as a heating source for heating the refrigerant liquid Vf. An evaporator heat source hot water valve 64 capable of adjusting the flow rate of the evaporator heat source hot water he flowing through the heat source pipe 61 is provided in the flow path for flowing the evaporator heat source hot water he after flowing through the heat source pipe 61. The low-temperature evaporator 60 is configured to operate at a pressure (dew point temperature) lower than that of the intermediate temperature evaporator 40, and the operating temperature is lower than that of the intermediate temperature evaporator 40.

  The low temperature absorber 50 and the low temperature evaporator 60 communicate with each other. The low temperature absorber 50 and the low temperature evaporator 60 communicate with each other so that the low temperature refrigerant vapor Vc generated in the low temperature evaporator 60 can be supplied to the low temperature absorber 50. The low-temperature absorber 50 and the low-temperature evaporator 60 typically communicate with each other above the low-concentration solution spray nozzle 52 and above the refrigerant liquid spray nozzle 62. Further, since the low temperature absorber 50 and the low temperature evaporator 60 are in communication with each other, they have substantially the same internal pressure.

  The regenerator 70 includes a heat source pipe 71 that forms a flow path of the regenerator heat source hot water hg as a regenerator heat source fluid, and a dilute solution spray nozzle 72 that sprays the dilute solution Sw. The regenerator heat source hot water hg flowing through the heat source pipe 71 of the regenerator 70 may be the same hot water as the evaporator heat source hot water he flowing through the heat source pipe 61 of the low temperature evaporator 60, and in that case, the regenerator heat source hot water hg flowed through the heat source pipe 61. It is good to be connected by piping (not shown) so that it may flow through the heat source pipe 71 later. Different heat source media may flow through the heat source tubes 61 and 71. The dilute solution spray nozzle 72 is disposed above the heat source pipe 71 so that the sprayed dilute solution Sw falls on the heat source pipe 71. In the regenerator 70, the sprayed dilute solution Sw is heated by the regenerator heat source hot water hg, whereby the refrigerant V evaporates from the dilute solution Sw to generate a high concentration solution Sa having an increased concentration. The regenerator heat source hot water hg is a heating source for heating the dilute solution Sw. The regenerator 70 is configured such that the generated high concentration solution Sa is stored in the lower part. A regenerator heat source hot water valve 74 capable of adjusting the flow rate of the regenerator heat source hot water hg flowing through the heat source pipe 71 is provided in the flow path for flowing the regenerator heat source hot water hg after flowing through the heat source pipe 71.

  The condenser 80 has a cooling water pipe 81 that forms a cooling medium flow path. The cooling water c as a cooling medium flows through the cooling water pipe 81. The condenser 80 is configured to introduce the regenerator refrigerant vapor Vg, which is the vapor of the refrigerant V generated in the regenerator 70, and to cool and condense it with the cooling water c. The cooling water c is a cooling source for cooling the regenerator refrigerant vapor Vg. The cooling water pipe 81 is disposed so that the regenerator refrigerant vapor Vg is not immersed in the condensed refrigerant liquid Vf so that the regenerator refrigerant vapor Vg can be directly cooled. A cooling water valve 81v capable of adjusting the flow rate of the cooling water c flowing through the cooling water pipe 81 is provided in the flow path for flowing the cooling water c after flowing through the cooling water pipe 81. One end of a refrigerant liquid pipe 88 that sends the condensed refrigerant liquid Vf toward the high-temperature evaporator 20, the intermediate-temperature evaporator 40, and the low-temperature evaporator 60 is connected to the condenser 80. The other end of the refrigerant liquid pipe 88 is connected to a refrigerant liquid pipe 82 connected to the high temperature evaporator 20 and a refrigerant liquid pipe 86 connected to the low temperature evaporator 60, and the refrigerant liquid Vf in the condenser 80 is heated to a high temperature. The evaporator 20, the intermediate temperature evaporator 40, and the low temperature evaporator 60 can be distributed. The refrigerant liquid pipe 88 is provided with a condensing refrigerant pump 89 for pumping the refrigerant liquid Vf. In the present embodiment, the refrigerant liquid pipe 88, the condensing refrigerant pump 89, and the refrigerant liquid pipes 82, 84, and 86 constitute a refrigerant liquid transport unit.

  The regenerator 70 and the condenser 80 are in communication with each other. By connecting the regenerator 70 and the condenser 80, the regenerator refrigerant vapor Vg generated in the regenerator 70 can be supplied to the condenser 80. The regenerator 70 and the condenser 80 communicate with each other in the upper gas phase portion. Further, the regenerator 70 and the condenser 80 communicate with each other, so that the internal pressure is substantially the same. The lower part of the regenerator 70 and the lower part of the condenser 80 are connected by a refrigerant liquid introduction pipe 78. The refrigerant liquid introduction pipe 78 has an end connected to a portion where the refrigerant liquid Vf is stored on the condenser 80 side, and passes through the can body on the regenerator 70 side above the liquid surface of the absorbing liquid S. The end is open. The refrigerant liquid introduction pipe 78 is provided with a refrigerant liquid introduction valve 78v that can block the flow of fluid. The refrigerant liquid introduction pipe 78 and the refrigerant liquid introduction valve 78v constitute a refrigerant liquid introduction part. In the present embodiment, the regenerator 70 and the condenser 80 are provided below the high temperature absorber 10, the high temperature evaporator 20, the intermediate temperature absorber 30, the intermediate temperature evaporator 40, the low temperature absorber 50, and the low temperature evaporator 60. It has been.

  The portion of the regenerator 70 where the high concentration solution Sa is stored and the high concentration solution spray nozzle 12 of the high temperature absorber 10 are connected by a high concentration solution tube 75. The high concentration solution pipe 75 is provided with a high concentration solution pump 76 that pumps the high concentration solution Sa in the regenerator 70 to the high concentration solution spray nozzle 12. The high-concentration solution pipe 75 and the high-concentration solution pump 76 are components of the concentrated solution transport unit. The storage unit 13 of the high temperature absorber 10 and the medium concentration solution spray nozzle 32 of the medium temperature absorber 30 are connected by a medium concentration solution tube 15. The medium concentration solution pipe 15 is provided with a medium concentration solution pump 16 that pumps the medium concentration solution Sb in the high temperature absorber 10 to the medium temperature absorber 30. The storage unit 33 of the intermediate temperature absorber 30 and the low concentration solution spray nozzle 52 of the low temperature absorber 50 are connected by a low concentration solution tube 35. The low concentration solution pipe 35 is provided with a low concentration solution pump 36 that pumps the low concentration solution Sc in the intermediate temperature absorber 30 to the low temperature absorber 50. The storage unit 53 of the low-temperature absorber 50 and the dilute solution spray nozzle 72 of the regenerator 70 are connected by a dilute solution tube 55.

  A high temperature heat exchanger 18 is disposed in the medium concentration solution tube 15 and the high concentration solution tube 75. The high temperature heat exchanger 18 is a device that exchanges heat between the medium concentration solution Sb flowing through the medium concentration solution tube 15 and the high concentration solution Sa flowing through the high concentration solution tube 75. An intermediate temperature heat exchanger 38 is disposed in the low concentration solution tube 35 and the high concentration solution tube 75. The intermediate temperature heat exchanger 38 is a device that exchanges heat between the low concentration solution Sc flowing through the low concentration solution tube 35 and the high concentration solution Sa flowing through the high concentration solution tube 75. A low temperature heat exchanger 58 is disposed in the dilute solution tube 55 and the high concentration solution tube 75. The low-temperature heat exchanger 58 is a device that performs heat exchange between the dilute solution Sw flowing through the dilute solution tube 55 and the high concentration solution Sa flowing through the high concentration solution tube 75.

  The absorption heat pump 1 is a gas-liquid separator that separates the heated water W heated by flowing through the heat transfer tube 11 of the high-temperature absorber 10 into the heated water vapor Wv and the heated water liquid Wq in addition to the main components described above. 90. The lower part of the gas-liquid separator 90 and one end of the heat transfer pipe 11 of the high-temperature absorber 10 are connected by a heated water liquid pipe 92 that guides the heated water liquid Wq to the heat transfer pipe 11. The side surface of the gas-liquid separator 90 whose inside is a gas phase portion and the other end of the heat transfer tube 11 are connected by a heated water tube 94 after heating that guides the heated water W to be heated to the gas-liquid separator 90. . Connected to the heated water liquid pipe 92 is a replenishment water pipe 95 for introducing replenishment water Ws as a replenishment fluid for supplementing the heated water W supplied to the outside of the system as steam. The makeup water pipe 95 is provided with a makeup water pump 96 that pumps the makeup water Ws toward the gas-liquid separator 90. In addition, a heated steam supply pipe 99 that supplies heated steam Wv to the outside of the system is connected to the upper part (typically the top) of the gas-liquid separator 90. The heated steam supply pipe 99 is provided with a safety valve 98. The safety valve 98 may be provided in the upper part (typically the top part) of the gas-liquid separator 90 in place of the heated steam pipe 99. The gas-liquid separator 90 may introduce a mixed fluid Wm in which a part of the heated water liquid Wq is evaporated in the heat transfer tube 11 and the heated water liquid Wq and the heated steam Wv are mixed. The water-liquid Wq may be guided to the gas-liquid separator 90, and the pressure may be reduced to partially vaporize the mixed fluid Wm to be gas-liquid separated.

  The control device 100 controls the operation of the absorption heat pump 1. The control device 100 is connected to each of the medium concentration solution pump 16, the low concentration solution pump 36, the low temperature refrigerant liquid pump 66, the high concentration solution pump 76, the condensing refrigerant pump 89, and the makeup water pump 96 through signal cables. It is configured to be able to adjust the start / stop and rotation speed. Further, the control device 100 is connected to the high temperature absorber pressure gauge 14P, the intermediate temperature absorber pressure gauge 34P, and the low temperature absorber pressure gauge 54P through signal cables, and the values detected by the pressure gauges 14P, 34P, 54P. Can be received as a signal. The control device 100 is connected to the evaporator heat source hot water valve 64, the regenerator heat source hot water valve 74, and the cooling water valve 81v through signal cables, respectively, and can adjust the opening degree of each valve 64, 74, 81v. It is configured to be able to. The control device 100 is connected to the refrigerant liquid introduction valve 78v by a signal cable, and is configured to be able to control opening and closing of the refrigerant liquid introduction valve 78v.

  With continued reference to FIG. 1, the operation of the absorption heat pump 1 will be described. During startup and steady operation of the absorption heat pump 1, the refrigerant liquid introduction valve 78v is closed, and the evaporator heat source hot water valve 64, the regenerator heat source hot water valve 74, and the flow rate adjustment valves 83, 85, 87 are opened. It has become. First, the refrigerant side cycle will be described. The condenser 80 receives the regenerator refrigerant vapor Vg generated in the regenerator 70, cools the regenerator refrigerant vapor Vg with the cooling water c flowing through the cooling water pipe 81, and condenses it into a refrigerant liquid Vf. The condensed refrigerant liquid Vf is pumped toward the high temperature evaporator 20, the medium temperature evaporator 40, and the low temperature evaporator 60 by the condensation refrigerant pump 89. The refrigerant liquid Vf pumped by the condensing refrigerant pump 89 flows through the refrigerant liquid pipe 88 and is divided into the refrigerant liquid pipe 82 and the refrigerant liquid pipe 86. A part of the refrigerant liquid Vf flowing through the refrigerant liquid pipe 82 flows into the refrigerant liquid pipe 84 in the middle, and the rest flows through the refrigerant liquid pipe 82 as it is and is introduced into the high-temperature refrigerant liquid supply pipe 22. The refrigerant liquid Vf flowing through the refrigerant liquid pipe 84 is introduced into the intermediate temperature refrigerant liquid supply pipe 42. The refrigerant liquid Vf flowing through the refrigerant liquid pipe 86 is introduced into the low temperature evaporator 60.

  The refrigerant liquid Vf introduced into the low temperature evaporator 60 is pumped to the refrigerant liquid spray nozzle 62 by the low temperature refrigerant liquid pump 66 and sprayed from the refrigerant liquid spray nozzle 62 toward the heat source pipe 61. The refrigerant liquid Vf sprayed from the refrigerant liquid spray nozzle 62 is heated and evaporated by the evaporator heat source hot water he flowing in the heat source pipe 61 to become a low-temperature refrigerant vapor Vc. The low-temperature refrigerant vapor Vc generated in the low-temperature evaporator 60 moves to the low-temperature absorber 50 that communicates with the low-temperature evaporator 60. On the other hand, the refrigerant liquid Vf introduced into the intermediate temperature refrigerant liquid supply pipe 42 flows into the heating pipe 51 of the low temperature absorber 50 by the action of the bubble pump. The refrigerant liquid Vf flowing into the heating pipe 51 is heated by the absorption heat generated when the low-temperature refrigerant vapor Vc moved from the low-temperature evaporator 60 is absorbed by the low-concentration solution Sc in the low-temperature absorber 50. Evaporates to medium temperature refrigerant vapor Vb. The intermediate temperature refrigerant vapor Vb generated in the heating pipe 51 flows through the intermediate temperature refrigerant vapor receiving pipe 44 and reaches the refrigerant gas-liquid separation cylinder 41. The intermediate temperature refrigerant vapor Vb flowing into the refrigerant gas-liquid separation cylinder 41 moves to the intermediate temperature absorber 30 communicating with the intermediate temperature evaporator 40 via the intermediate temperature refrigerant vapor pipe 49. The refrigerant liquid Vf introduced into the high-temperature refrigerant liquid supply pipe 22 flows into the heating pipe 31 of the intermediate temperature absorber 30 by the action of the bubble pump. The refrigerant liquid Vf flowing into the heating pipe 31 is heated by the absorption heat generated when the intermediate temperature refrigerant vapor Vb moved from the intermediate temperature evaporator 40 is absorbed by the intermediate concentration solution Sb in the intermediate temperature absorber 30, and this heating is performed. Evaporates to a high-temperature refrigerant vapor Va. The high-temperature refrigerant vapor Va generated in the heating pipe 31 flows through the high-temperature refrigerant vapor receiving pipe 24 and reaches the refrigerant gas-liquid separation cylinder 21. The high-temperature refrigerant vapor Va flowing into the refrigerant gas-liquid separation cylinder 21 moves to the high-temperature absorber 10 that communicates with the high-temperature evaporator 20 via the high-temperature refrigerant vapor pipe 29.

  Next, the cycle on the absorption liquid side of the absorption heat pump 1 will be described. In the high temperature absorber 10, the high concentration solution Sa is sprayed from the high concentration solution spray nozzle 12, and the sprayed high concentration solution Sa absorbs the high temperature refrigerant vapor Va that has moved from the high temperature evaporator 20. The high-concentration solution Sa that has absorbed the high-temperature refrigerant vapor Va is reduced in concentration to become a medium-concentration solution Sb. In the high-temperature absorber 10, heat of absorption is generated when the high-concentration solution Sa absorbs the high-temperature refrigerant vapor Va. The heated water liquid Wq flowing through the heat transfer tube 11 is heated by the absorbed heat. Here, the effect | action around the gas-liquid separator 90 for taking out the to-be-heated water vapor | steam Wv is demonstrated.

  The gas-liquid separator 90 is introduced with make-up water Ws from outside the system through a make-up water pipe 95. The makeup water Ws is pumped through the makeup water pipe 95 by the makeup water pump 96 and introduced into the heated water liquid pipe 92. The makeup water Ws introduced into the heated water liquid pipe 92 joins with the heated water liquid Wq flowing from the lower part of the gas-liquid separator 90 as the heated water liquid Wq, and is absorbed at a high temperature by the action of the bubble pump. It flows into the heat transfer tube 11 of the vessel 10. The heated liquid Wq flowing into the heat transfer tube 11 is heated by the above-described absorbed heat in the high-temperature absorber 10. The heated liquid Wq heated by the heat transfer tube 11 is supplied to the gas-liquid separator 90 as a mixed fluid Wm partially evaporated to become heated steam Wv or as a heated liquid Wq whose temperature has increased. After being heated, it flows through the heated water pipe 94. When the heated water liquid Wq whose temperature has risen flows through the heated water pipe 94 after heating, the heated water liquid Wq is introduced into the introduction portion to the gas-liquid separator 90 when introduced into the gas-liquid separator 90. The pressure is reduced by a pressure reducing device (not shown) such as a provided valve or orifice, and the mixed fluid Wm partially evaporated to be heated steam Wv is introduced into the gas-liquid separator 90. In the mixed fluid Wm introduced into the gas-liquid separator 90, the heated water liquid Wq and the heated water vapor Wv are separated. The separated heated liquid Wq is stored in the lower part of the gas-liquid separator 90 and sent again to the heat transfer tube 11 of the high-temperature absorber 10. On the other hand, the separated heated steam Wv flows out to the heated steam supply pipe 99 and is supplied to the steam utilization place. In the present embodiment, heated steam Wv of about 0.8 MPa (gauge pressure) is supplied.

  Returning to the description of the cycle on the absorption liquid side of the absorption heat pump 1 again. The high-concentration solution Sa that has absorbed the high-temperature refrigerant vapor Va by the high-temperature absorber 10 is reduced in concentration to become a medium-concentration solution Sb and stored in the storage unit 13. The intermediate concentration solution Sb in the reservoir 13 flows through the intermediate concentration solution tube 15 toward the intermediate temperature absorber 30 by the operation of the intermediate concentration solution pump 16, and exchanges heat with the high concentration solution Sa in the high temperature heat exchanger 18. After the decrease, the medium concentration solution spray nozzle 32 is reached. Thus, in this Embodiment, the absorption liquid S in the high temperature absorber 10 is directly introduce | transduced into the intermediate temperature absorber 30 (without passing through another absorber). It should be noted that the internal pressure of the high temperature absorber 10 is higher than the internal pressure of the intermediate temperature absorber 30, and even if the intermediate concentration solution pump 16 is not operating, the medium concentration solution in the high temperature absorber 10 is caused by the difference between the internal pressures of both. When Sb can be conveyed to the intermediate temperature absorber 30, the intermediate concentration solution pump 16 may be stopped.

  In the intermediate temperature absorber 30, the intermediate concentration solution Sb is dispersed from the intermediate concentration solution spray nozzle 32, and the dispersed intermediate concentration solution Sb absorbs the intermediate temperature refrigerant vapor Vb moved from the intermediate temperature evaporator 40. The medium concentration solution Sb that has absorbed the intermediate temperature refrigerant vapor Vb is reduced in concentration to become a low concentration solution Sc and stored in the storage unit 33. In the intermediate temperature absorber 30, heat of absorption is generated when the intermediate concentration solution Sb absorbs the intermediate temperature refrigerant vapor Vb. As described above, the refrigerant liquid Vf flowing through the heating pipe 31 is heated by this absorbed heat. The low-concentration solution Sc in the reservoir 33 flows through the low-concentration solution pipe 35 toward the low-temperature absorber 50 by the operation of the low-concentration solution pump 36, and exchanges heat with the high-concentration solution Sa in the intermediate temperature heat exchanger 38. After the decrease, the low concentration solution spray nozzle 52 is reached. Thus, in the present embodiment, the absorbing liquid S in the high temperature absorber 10 is indirectly introduced into the low temperature absorber 50 via the intermediate temperature absorber 30. The internal pressure of the intermediate temperature absorber 30 is higher than the internal pressure of the low temperature absorber 50, and even if the low concentration solution pump 36 is not operating, the low concentration solution Sc in the intermediate temperature absorber 30 is caused by the difference in internal pressure between the two. Can be transported to the low temperature absorber 50, the low concentration solution pump 36 may be stopped.

  In the low temperature absorber 50, the low concentration solution Sc that has flowed into the low concentration solution spray nozzle 52 is sprayed toward the heating pipe 51. The dispersed low-concentration solution Sc absorbs the low-temperature refrigerant vapor Vc that has moved from the low-temperature evaporator 60. The low-concentration solution Sc that has absorbed the low-temperature refrigerant vapor Vc is reduced in concentration to become a dilute solution Sw. In the low-temperature absorber 50, absorption heat is generated when the low-concentration solution Sc absorbs the low-temperature refrigerant vapor Vc. As described above, the absorbed heat heats the refrigerant liquid Vf flowing through the heating pipe 51 to generate the intermediate temperature refrigerant vapor Vb. The dilute solution Sw in the low-temperature absorber 50 flows through the dilute solution tube 55 toward the regenerator 70 by gravity. At this time, the dilute solution Sw is introduced into the regenerator 70 after the low temperature heat exchanger 58 exchanges heat with the high concentration solution Sa to lower the temperature. Thus, in the present embodiment, the absorbing liquid S in the high temperature absorber 10 is indirectly introduced into the regenerator 70 via the intermediate temperature absorber 30 and the low temperature absorber 50.

  The dilute solution Sw sent to the regenerator 70 is sprayed from the dilute solution spray nozzle 72. The dilute solution Sw sprayed from the dilute solution spray nozzle 72 is heated by the regenerator heat source hot water hg flowing in the heat source pipe 71 (about 80 ° C. in the present embodiment), and the refrigerant in the sprayed dilute solution Sw evaporates. As a result, it becomes a high concentration solution Sa and is stored in the lower part of the regenerator 70. On the other hand, the refrigerant V evaporated from the dilute solution Sw moves to the condenser 80 as the regenerator refrigerant vapor Vg. The high concentration solution Sa stored in the lower part of the regenerator 70 is pumped by the high concentration solution pump 76 to the high concentration solution spray nozzle 12 of the high temperature absorber 10 through the high concentration solution pipe 75. The high-concentration solution Sa flowing through the high-concentration solution tube 75 heat-exchanges with the dilute solution Sw in the low-temperature heat exchanger 58 to increase the temperature, and heat-exchanges with the low-concentration solution Sc in the intermediate-temperature heat exchanger 38 to further increase the temperature. Then, the high-temperature heat exchanger 18 exchanges heat with the medium-concentration solution Sb to further increase the temperature, and then flows into the high-temperature absorber 10 and is sprayed from the high-concentration solution spray nozzle 12. Thereafter, the same cycle is repeated.

  When the absorption heat pump 1 operates as described above, the gas-liquid separator is introduced by the introduction of the evaporator heat source hot water he and the regenerator heat source hot water hg, and the absorption heat generated by the absorption liquid S absorbing the vapor of the refrigerant V. 90 and the internal pressure of each absorber can body 14, 34, 54 increase, and some of them exceed atmospheric pressure. The can body exceeding the atmospheric pressure corresponds to a pressure vessel, and the internal pressure is required to be kept below the maximum operating pressure. Since the gas-liquid separator 90 is provided with a safety valve 98 in the heated steam supply pipe 99 (or the upper part of the gas-liquid separator 90) communicating with the inside thereof, the safety valve 98 is opened when the maximum operating pressure is exceeded, Keep below maximum working pressure. On the other hand, since each absorber can body 14, 34, 54 has an internal pressure of less than atmospheric pressure when the absorption heat pump 1 is stopped, when a safety valve is provided in a portion communicating with the inside of the can barrel, There is a possibility that air may enter the inside through the safety valve, and there is a possibility that the output may be reduced due to air mixing and corrosion inside the can body may proceed. Therefore, in the absorption heat pump 1 according to the present embodiment, the following control is performed so that the inside of the can body can be prevented from exceeding a predetermined pressure without providing a safety valve in a portion communicating with the inside of the can body. Is going to do.

  That is, the control device 100 determines the pressures detected by the high-temperature absorber pressure gauge 14P, the intermediate-temperature absorber pressure gauge 34P, and the low-temperature absorber pressure gauge 54P during the operation of the absorption heat pump 1, respectively. It is determined whether or not the above has been reached. The predetermined pressure is, for example, 0.35 MPa (gauge pressure) in the high temperature absorber can body 14, 0.1 MPa (gauge pressure) in the intermediate temperature absorber can body 34, and 0.05 MPa in the low temperature absorber can body 54. (Gauge pressure). When any one of the pressures detected by the pressure gauges 14P, 34P, 54P becomes equal to or higher than a predetermined pressure, the control device 100 stops the low-temperature refrigerant liquid pump 66 and the condensing refrigerant pump 89. When the low-temperature refrigerant liquid pump 66 is stopped, the distribution of the refrigerant liquid Vf from the refrigerant liquid spray nozzle 62 is stopped, so the generation of the low-temperature refrigerant vapor Vc is stopped, and the generation of heat absorbed in the low-temperature absorber 50 is stopped. Thereby, the rise in the pressure in the low temperature absorber 50 is suppressed. When the condensing refrigerant pump 89 is stopped, the supply of the refrigerant liquid Vf to the low temperature evaporator 60 is stopped, and the supply of the refrigerant liquid Vf to the intermediate temperature refrigerant liquid supply pipe 42 and the high temperature refrigerant liquid supply pipe 22 is also stopped. Then, the generation of the intermediate temperature refrigerant vapor Vb in the intermediate temperature evaporator 40 and the generation of the high temperature refrigerant vapor Va in the high temperature evaporator 20 are stopped, and the generation of the absorption heat in the intermediate temperature absorber 30 and the generation of the absorption heat in the high temperature absorber 10 are stopped. Thereby, the rise in the pressure in the intermediate temperature absorber 30 and the rise in the pressure in the high temperature absorber 10 are suppressed. And in each absorber 10, 30, and 50, after generation | occurrence | production of absorption heat stops, temperature falls with progress of time and internal pressure also falls along with it.

  At this time, in the present embodiment, the operation of the high concentration solution pump 76 is continued, and the operation of the medium concentration solution pump 16 and / or the low concentration solution pump 36 is also continued as necessary. In other words, in the present embodiment, when any one of the pressures detected by the pressure gauges 14P, 34P, 54P exceeds a predetermined pressure, the refrigerant to each evaporator 20, 40, 60 While stopping the introduction of the liquid Vf, the introduction of the absorbing liquid S to each of the absorbers 10, 30, and 50 is continued. When the introduction of the high-concentration solution Sa to the high-temperature absorber 10 is continued while the introduction of the refrigerant liquid Vf to the high-temperature evaporator 20 is stopped, the high-temperature refrigerant vapor Va remaining in the high-temperature evaporator 20 moves to the high-temperature absorber 10. Therefore, the amount of refrigerant vapor in the high-temperature absorber can body 14 and the refrigerant gas-liquid separation cylinder 21 communicating with the high-concentration solution Sa is reduced, and the pressure in the high-temperature absorber can body 14 is reduced. It can be reduced relatively quickly. Similarly, if the introduction of the absorbing liquid into the intermediate temperature absorber 30 and the low temperature absorber 50 is continued, the pressure in the intermediate temperature absorber can body 34 and the pressure in the low temperature absorber can body 54 can be reduced relatively quickly. .

  FIG. 2A shows the gas-liquid when the introduction of the absorbing liquid S to each of the absorbers 10, 30, 50 is continued while the introduction of the refrigerant liquid Vf to each of the evaporators 20, 40, 60 is stopped. An example of the change of the internal pressure of the separator 90, the high temperature absorber can body 14, and the intermediate temperature absorber can body 34 is shown. In the graph shown in FIG. 2A, pressure is plotted on the vertical axis and time is plotted on the horizontal axis, line P90 shows the internal pressure of the gas-liquid separator 90, line P10 shows the internal pressure of the high-temperature absorber can body 14, P30 shows the internal pressure of the intermediate temperature absorber can body 34, respectively. In the graph shown in FIG. 2A, since the internal pressure of the intermediate temperature absorber can body 34 gradually increases and reaches a predetermined pressure at time t1, the refrigerant liquid Vf to each of the evaporators 20, 40, 60 is shown. It shows the situation where the introduction of. In the example shown in FIG. 2A, after the introduction of the refrigerant liquid Vf to each of the evaporators 20, 40, 60 is stopped at time t1, the gas-liquid separator 90, the high-temperature absorber can body 14, and the intermediate temperature absorption are performed. It can be seen that the internal pressure of the container can body 34 quickly decreases.

  As explained above, according to the absorption heat pump 1 according to the present embodiment, when any one of the pressures detected by the pressure gauges 14P, 34P, 54P is equal to or higher than a predetermined pressure, Since the introduction of the refrigerant liquid Vf to the evaporators 20, 40, 60 is stopped, an increase in the internal pressure of each absorber can body 14, 34, 54 can be suppressed without providing a safety valve. In addition, while the introduction of the refrigerant liquid Vf to each of the evaporators 20, 40, 60 is stopped, the introduction of the absorption liquid S to each of the absorbers 10, 30, 50 is continued, so that each absorber can body 14, The internal pressures 34 and 54 can be reduced relatively quickly.

  In the above description, when at least one of the pressures detected by the pressure gauges 14P, 34P, 54P becomes equal to or higher than a predetermined pressure, the introduction of the refrigerant liquid Vf to the evaporators 20, 40, 60 is stopped. However, instead of stopping the introduction of the refrigerant liquid Vf to each of the evaporators 20, 40, 60, the introduction of the absorbing liquid S to each of the absorbers 10, 30, 50 may be stopped. In order to stop the introduction of the absorbing solution into each of the absorbers 10, 30, and 50, the operation of the high concentration solution pump 76, the medium concentration solution pump 16, and the low concentration solution pump 36 may be stopped. When these pumps 76, 16, 36 are stopped, the high-temperature absorber 10 stops spraying the high-concentration solution Sa from the high-concentration solution spray nozzle 12, so that the absorption of the high-temperature refrigerant vapor Va by the high-concentration solution Sa stops. The generation of absorbed heat in the high-temperature absorber 10 stops. Thereby, the rise in the pressure in the high temperature absorber 10 is suppressed. Similarly, in the intermediate temperature absorber 30, the application of the intermediate concentration solution Sb from the intermediate concentration solution spray nozzle 32 is stopped, and the generation of heat of absorption in the intermediate temperature absorber 30 stops. In the low temperature absorber 50, the low concentration solution spray nozzle is stopped. The spraying of the low-concentration solution Sc from 52 stops and the generation of heat of absorption in the low-temperature absorber 50 stops. Thereby, the rise in the pressure in the intermediate temperature absorber 30 and the rise in the pressure in the low temperature absorber 50 are suppressed. And in each absorber 10, 30, and 50, after generation | occurrence | production of absorption heat stops, temperature falls with progress of time and internal pressure also falls along with it.

  FIG. 2B shows the gas-liquid when the introduction of the refrigerant liquid Vf to each of the evaporators 20, 40, 60 is continued while the introduction of the absorbing liquid S to each of the absorbers 10, 30, 50 is stopped. An example of the change of the internal pressure of the separator 90, the high temperature absorber can body 14, and the intermediate temperature absorber can body 34 is shown. The graph shown in FIG. 2 (B), like the graph shown in FIG. 2 (A), takes pressure on the vertical axis and time on the horizontal axis, and the diagrams P90, P10, and P30 are gas-liquid, respectively. The internal pressures of the separator 90, the high temperature absorber can body 14, and the intermediate temperature absorber can body 34 are shown. In the graph shown in FIG. 2B, since the internal pressure of the intermediate temperature absorber can body 34 gradually increases and reaches a predetermined pressure at time t2, each pump 76, 16, and 36 is stopped. The situation where the introduction of the absorbing liquid into the absorbers 10, 30, and 50 is stopped is shown. In the example shown in FIG. 2B, after the pumps 76, 16, and 36 are stopped at time t2, the internal pressure temporarily rises in the high temperature absorber can body 14 and the intermediate temperature absorber can body 34, It can be seen that the internal pressures of the liquid separator 90, the high temperature absorber can body 14, and the intermediate temperature absorber can body 34 are rapidly reduced. The internal pressure temporarily rises in the high-temperature absorber can body 14 and the intermediate-temperature absorber can body 34 when the introduction of the absorbing liquid to each absorber 10, 30, 50 is stopped. This is because the absorption liquid remaining in the absorber can bodies 14, 34, 54 has flowed for a while due to the internal pressure difference between the absorber can bodies 14, 34, 54 after the stop of 36, 36.

  Alternatively, when at least one of the pressures detected by each of the pressure gauges 14P, 34P, 54P becomes equal to or higher than a predetermined pressure, the introduction of the refrigerant liquid Vf to each of the evaporators 20, 40, 60 is stopped, Instead of performing one of stopping the introduction of the absorbing liquid S to each of the absorbers 10, 30, and 50, both of them may be performed. Further, the evaporator heat source hot water valve 64 is superimposed on the stop of introduction of the refrigerant liquid Vf to each evaporator 20, 40, 60 and / or the stop of introduction of the absorbent S to each absorber 10, 30, 50. And / or adjusting the opening of the regenerator heat source hot water valve 74 and / or the cooling water valve 81v to introduce part or all of the evaporator heat source hot water he into the low temperature evaporator 60 and / or regenerate the regenerator 70. The introduction of a part or the whole of the heat source hot water hg and / or the introduction of a part or the whole of the cooling water c to the condenser 80 may be stopped. When the introduction of part or all of the evaporator heat source hot water he to the low temperature evaporator 60 is stopped, the generation of the low temperature refrigerant vapor Vc is suppressed, the generation of the absorption heat in the low temperature absorber 50 is suppressed, and each absorber 10 is suppressed. , 30, 50 contributes to the suppression of the increase in internal pressure. On the other hand, when the introduction of part or all of the regenerator heat source hot water hg to the regenerator 70 is stopped, the concentration of the absorption liquid S in the regenerator 70 is suppressed, and the generation of heat of absorption in the high temperature absorber 10 is suppressed. It will contribute to the suppression of the increase in the internal pressure of each absorber 10, 30, 50. Further, when the introduction of a part or all of the cooling water c to the condenser 80 is stopped, the amount of heat released from the condenser 80 decreases, and the dew point at which the regenerator refrigerant vapor Vg condenses rises. In the regenerator 70 that communicates with the regenerator 70, the boiling temperature of the absorbing liquid S rises, the amount of heating to the absorbing liquid S by the regenerator heat source hot water hg decreases, and the concentration of the absorbing liquid S is suppressed. Generation | occurrence | production is suppressed and it will contribute to suppression of the raise of the internal pressure of each absorber 10,30,50.

  Further, when at least one of the pressures detected by each of the pressure gauges 14P, 34P, 54P becomes equal to or higher than a predetermined pressure, the introduction of the refrigerant liquid Vf to each of the evaporators 20, 40, 60 is stopped and / or The introduction and / or regeneration of part or all of the evaporator heat source hot water he to the low-temperature evaporator 60 is superimposed on or in addition to the suspension of the introduction of the absorbent S to the absorbers 10, 30, 50. The refrigerant liquid introduction valve 78v is opened so as to overlap the stoppage of part or all of the regenerator heat source hot water hg to the condenser 70 and / or the stoppage of part or all of the cooling water c to the condenser 80. The refrigerant liquid Vf in the condenser 80 may be introduced into the regenerator 70 via the refrigerant liquid introduction pipe 78. When the refrigerant liquid Vf in the condenser 80 is introduced into the regenerator 70, the absorption liquid S in the regenerator 70 having the highest concentration because the absorption liquid S no longer absorbs the vapor of the refrigerant V can be diluted. , The absorption liquid S can be prevented from crystallizing. When the introduction of the refrigerant liquid Vf to each evaporator 20, 40, 60 is stopped, the vapor of the refrigerant V does not flow into each absorber 10, 30, 50, and the absorption liquid at the outlet of each absorber 10, 30, 50 When the concentration of S remains high and the absorbing liquid S flows into the regenerator 70, the concentration of the absorbing liquid S in the regenerator 70 increases. Alternatively, when the introduction of the absorbing liquid S to each of the absorbers 10, 30, and 50 is stopped, the flow of the absorbing liquid S in the regenerator 70 is also stopped, and the absorbing liquid S in the regenerator 70 is supplied from the regenerator heat source hot water hg. Concentrated by the residual heat, the concentration of the absorbing liquid S in the regenerator 70 increases. By opening the refrigerant liquid introduction valve 78v and introducing the refrigerant liquid Vf in the condenser 80 into the regenerator 70, the crystals of the absorbing liquid S in the regenerator 70 can be suppressed. If the refrigerant liquid Vf in the condenser 80 is not introduced into the regenerator 70 because there is no risk of crystallization of the absorbing liquid S, the refrigerant liquid introduction pipe 78 and the refrigerant liquid introduction valve 78v are provided. It may be omitted.

  In the above description, the internal pressures of the absorber can bodies 14, 34, and 54 are directly detected by the pressure gauges 14P, 34P, and 54P, but the high-temperature absorber 10, the high-temperature evaporator 20, and the intermediate-temperature absorber 30 are used. And the intermediate temperature evaporator 40, the low temperature absorber 50, and the low temperature evaporator 60 are in communication with each other, so that the internal pressures of the evaporators 20, 40, 60 are detected to indirectly detect the absorber can bodies 14, 34. , 54 may be detected, and in each of the evaporators 20, 40, 60, the saturation temperature of the refrigerant is detected and converted into a pressure indirectly, whereby each absorber can body 14, 34, The internal pressure of 54 may be detected.

  In the above description, the high-concentration solution Sa is sent from the regenerator 70 to the high-temperature absorber 10, and then the absorbent is sent in series to the intermediate-temperature absorber 30 and the low-temperature absorber 50. It is good also as sending absorption liquid to absorber 10, 30, 50 in parallel.

  In the above description, the absorption heat pump 1 is a three-stage temperature rising type, but it may be a two-stage temperature rising type or a single-stage temperature rising type. In the case of the two-stage temperature rising type, the structure around the intermediate temperature absorber 30 and the intermediate temperature evaporator 40 is omitted from the structure of the three-stage temperature rising type absorption heat pump 1, and the high-temperature refrigerant liquid supply pipe 22 and the high temperature of the high-temperature evaporator 20 are omitted. The refrigerant vapor receiving pipe 24 is connected to the heating pipe 51 of the low-temperature absorber 50, the medium-concentration solution pipe 15 is connected to the low-concentration solution spray nozzle 52, and the medium-concentration solution Sb in the high-temperature absorber 10 is directly (other absorptions). What is necessary is just to comprise so that it may introduce | transduce into the low temperature absorber 50 (without going through a device). In the case of the single-stage temperature rising type, the high-temperature evaporator 20 and the low-temperature absorber 50 are further omitted from the configuration of the above-described two-stage temperature rising type absorption heat pump, and the low-temperature refrigerant vapor Vc generated in the low-temperature evaporator 60 is absorbed at high temperature. The medium concentration solution tube 15 is connected to the dilute solution spray nozzle 72 in the regenerator 70 and the medium concentration solution Sb in the high temperature absorber 10 is directly connected (other absorbers are connected). It may be configured to be introduced into the regenerator 70 (without going through).

DESCRIPTION OF SYMBOLS 1 Absorption heat pump 10 High temperature absorber 11 Heat transfer tube 12 High concentration solution spray nozzle 14 High temperature absorber can body 14P High temperature absorber pressure gauge 20 High temperature evaporator 30 Medium temperature absorber 31 Heating tube 32 Medium concentration solution spray nozzle 34 Medium temperature absorber can Body 34P Medium temperature absorber pressure gauge 40 Medium temperature evaporator 50 Low temperature absorber 51 Heating pipe 52 Low concentration solution spray nozzle 54 Low temperature absorber can body 54P Low temperature absorber pressure gauge 60 Low temperature evaporator 70 Regenerator 78 Refrigerant liquid introduction pipe 78v Refrigerant Liquid introduction valve 80 Condenser 75 High-concentration solution pipe 76 High-concentration solution pump 82, 84, 86, 88 Refrigerant liquid pipe 89 Condensing refrigerant pump 100 Controller he Evaporator heat source hot water hg Regenerator heat source hot water Sa High concentration solution Sb Medium concentration Solution Sc Low concentration solution Sw Dilute solution Va High temperature refrigerant vapor Vb Medium temperature refrigerant vapor Vc Low temperature refrigerant vapor Vf Refrigerant liquid Vg Regenerator refrigerant vapor q-be-heated water solution

Claims (5)

A heated fluid flow path, an absorbent supply section that supplies an absorbent toward the heated fluid flow path, and an absorber can body that houses the heated fluid flow path and the absorbent supply section An absorber that heats the fluid flowing through the heated fluid flow path with absorption heat generated when the absorption liquid supplied from the absorption liquid supply unit absorbs the vapor of the refrigerant;
A regenerator for introducing a dilute solution, which is an absorption liquid having a reduced concentration by absorbing vapor of the refrigerant in the absorber, and heating the desorbed liquid to release the refrigerant from the dilute solution to increase the concentration of the absorption liquid; ;
A concentrated solution transport unit that guides the absorbing solution whose concentration is higher than that of the diluted solution in the regenerator to the absorbing solution supply unit;
A condenser for introducing the vapor of the refrigerant separated from the dilute solution in the regenerator, cooling and condensing the refrigerant, and generating a liquid of the refrigerant;
An evaporator that introduces the liquid of the refrigerant generated in the condenser, heats and evaporates it to generate vapor of the refrigerant to be supplied to the absorber;
A refrigerant liquid transport section for guiding the refrigerant liquid of the condenser to the evaporator;
A pressure detector for directly or indirectly detecting the internal pressure of the absorber can body;
A control device that stops at least one of introduction of the absorption liquid into the absorption liquid supply unit and introduction of the refrigerant liquid into the evaporator when the pressure detected by the pressure detector is equal to or higher than a predetermined pressure. And comprising:
Absorption heat pump. When the pressure detected by the pressure detector is equal to or higher than a predetermined pressure, the control device stops introduction of the refrigerant liquid into the evaporator, while the absorption liquid supply to the absorption liquid supply unit is stopped. Continue the introduction;
The absorption heat pump according to claim 1. The absorber comprises a high temperature absorber and a low temperature absorber having a lower operating pressure than the high temperature absorber;
The evaporator comprises a high temperature evaporator and a low temperature evaporator having a lower operating pressure than the high temperature evaporator;
The refrigerant vapor generated in the low temperature evaporator is introduced into the low temperature absorber and the refrigerant vapor generated in the high temperature evaporator is introduced into the high temperature absorber;
The pressure detector is configured to directly or indirectly detect an internal pressure of the absorber can body of each of the high temperature absorber and the low temperature absorber;
The predetermined pressure is set individually for the high temperature absorber and the low temperature absorber;
The absorption heat pump according to claim 1 or 2. When the pressure detected by the pressure detector is equal to or higher than a predetermined pressure, the control device introduces a part or all of the heating source to the regenerator, or part or all of the heating source to the evaporator. And at least one of the introduction of part or all of the cooling source to the condenser is stopped;
The absorption heat pump according to any one of claims 1 to 3. A refrigerant liquid introduction section that allows the refrigerant liquid of the condenser to be introduced into the regenerator;
The control device starts introducing the refrigerant liquid of the condenser into the regenerator when the pressure detected by the pressure detector is equal to or higher than a predetermined pressure;
The absorption heat pump according to any one of claims 1 to 4.

Images